Hydraulic back gauge for paper cutters



Aug. 24, 1954 s. FRANKEL 2,637,011

HYDRAULIC BACK GAUGE FOR PAPER CUTTERS Filed March 25, 1950 4 Sheets-Sheet l INVENTOR SYDNEY FRANKEL.

ATTORN EYS Aug. 24, 195.4 s. FRANKEL 2,637,011

HYDRAULIC BACK GAUGE FOR PAPER .CUTTERS Filed March 25, 1950 4 Sheets- Sheet z BY 76 Wrw ATTORNEYS Aug. 24, 1954 s. FRANKEL 2,587,01I

HYDRAULIC BACK GAUGE FOR PAPER CUTTERS Filed March 25, 1950 4 Sheets-Sheet 4 ATTORNEYS Patented Aug. 24, 1954 ATENT OFFICE 2,687,011 HYDRAULIC BACK GAUGE FOR PAPER CUTTER Sydney Frankel, Ridgefield Park, N. J assignor to E.

P. Lawson 00., Inc.,

New York, N. Y., a

corporation of New York Application March 25, 1950, Serial No. 151,936

3 Claims.

My present invention relates to a hydraulically operated back gauge for paper cutters and more particularly to a back gauge operating mechanism adapted to move the back gauge through a series of steps to permit the cutter to perform a series of cuts on a paper stack.

For this purpose in order to obtain speed in operation, the back gauge should move rapidly between cuts. But to ensure that the paper stack will stop at an accurate predetermined cutting position for each cut, the back gauge must be slowed up just before the cutting position so that when it is brought to a stop, the paper stack will not coast beyond the stop position.

The object of my invention, therefore, is the provision of novel hydraulic back gauge operating means which will move the back gauge rapidly between cuts, will slow the back gauge down just before a. cutting position is reached and halt the back gauge at the cutting position.

A further object of my invention is .the provision of control means for the back gauge of such nature that these operations may be automatically performed.

Another object, to carry out the foregoing objects, is to provide solenoid operated valve elements for the hydraulic operating mechanism so that the foregoing automatic control may be carried out.

Another object is the arrangement of the hydraulic operating means so that, by a shift in valves, it may :be reversed to return the back gauge to its initial position.

The foregoing and many other objects of my invention will become apparent from the following description and drawings in which:

Figure l is a side view of my novel hydraulically operated back gauge mechanism.

Figure 2 is a rear view of the mechanism of Figure 1.

Figure 3 is a top view of the mechanism of Figure 1 taken from line 3-3 of Figure 2.

Figures 4 to 7 are schematic views of the hydraulic operating mechanism illustrating the operation of the mechanism for fast forward motion (Figure 4), slow forward motion (Figure 5), stopping of the back gauge (Figure 6) and reverse movement of the back gauge (Figure 7).

Referring first to Figures 1 to 3, the cutting machine in connection with which my novel back gauge is used is of the general type shown in Patent No. 2,574,501, issued November 13, 1951, and the back gauge operates for the general purposes therein described.

Thus, the machine is provided with the side frame base casting 20.0 which carries the bed plate or support Hill for a stack of paper. The back gauge 29! rides on the bed plate lull and is provided with a bracket 282 extending downwardly through a longitudinal slot in bed plate lib] terminating in a nut 203 which engages the longitudinal screw 2:114 supported in appropriate bearings 2 95, 206 at the front and back of the bed plate I00.

The front of screw 204 is provided with the hand wheel 21-0 for manual rotation of screw 204 to obtain manual adjustment of the back gauge 281 when required. Cable 212 extending over guide pulleys 213, 214, 215 is connected to the back gauge 25! and extends up to the indicating and back gauge stop mechanism 22E? mounted on the top cross bar '22I of the machine and operating in the manner described in Patent No. 2,628,680, issued February 17, 1953.

The side frame members 2% are extended up at 225 to furnish vertical slide ways for a knife bar and clamp which operate in the manner described in Patent No. 2,574,501 issued Nov. 13, 1951. The operating mechanism for the knife bar and clamp are, as described in the aforesaid patents, mounted between the side frame members 225.

The feed screw 20:3 for the back gauge 201 may be rotated for automatic (non-manual) operation by the pulley operating mechanism shown in the figures.

The reservoir tank 8| for the hydraulic fluid used in the system is located rearwardly of the base frame casting 260. An accumulator cylinder 82 is mounted in tank 8! and immersed in the reservoir oil; this obviates the necessity for extended connections between the reservoir BI and the accumulator cylinder :82.

Bracket 84 supported on reservoir tank 8! carries a pump 83 driven by pulley 85 and V-belt 87 from pulley 1:63 of electric motor 85 mounted on bracket H carried by the base casting 2%.

Pump t3 draws hydraulic fluid from reservoir tank ti through the pipe 8%, filters 89 and 9t and pipe "I9 (see Figure 2) and discharges the hydraulic fluid through flexible hose 91 into the main relief valve :92.

Main relief valve '92 controls the pressure available to drive the back gauge Zili as hereinafter described. Relief valve :92 may, therefore, be adjusted to any selected pressure; its overflow is discharged through pipe 93 directly back to the reservoir tank 8].

Flexiblehose 94 conducts hydraulic fluid under pressure from the main relief valve 92 to the H driven in turn by the hydraulic 3 micro-filter 96 and then through pipe 94a to the solenoid valve and sub-base block 95.

Solenoid valve sub-base block 95 is provided with suitable passages hereinafter described in connection with Figures 4 to 7 to establish various hydraulic fluid circuits through the four-way solenoid valve 9'! and the two-way solenoid valve 98.

Pipes 99a and 9% connect the solenoid valve sub-base block at with the fluid motor I84. The speed and direction of the fluid motor depends on the setting of solenoid valves 91 and 98.

Flexible hose I85 connects the valve sub-base block 85 to pipe I86 which enters the high pressure chamber I3 of accumulator 82. The low pressure chamber M of accumulator 82 communicates through opening I5 with the low pressure fluid in reservoir 8 I.

Piston III is urged by compression spring II in chamber I4 toward the right with respect to Figure 2 to create an initial elevated pressure in chamber I3 of accumulator 82. Piston I6 thus forms the boundary between chambers 13 and 14.

As pressure in chamber I3 increases, piston It i forced to the left against spring 'I'I further compressing the same. A relief path for excess pressure in chamber I3 is provided by the recess I8 in accumulator 82. When the piston, on being forced to the left with respect to Figure 2, reaches recess I8, the excess fluid under pressure may escape to the low pressure chamber M until the spring II can move piston I6 back to the right to close the recess I8;

The fluid motor I04 is connected by pulley BI] and belt 6I to pulley 62 on stub shaft 63. Pulley 64 on stub shaft 63 is connected by belt 65 to pulley II on screw 204 which drives the back gauge 28 I.

Thus, the back gauge is driven by the fluid motor I04 which in turn responds to the direction, pressure and rate of flow of the hydraulic fluid as hereinafter described in connection with Figures 4 to '7.

Motor 86 and pump 83 operate constantly so that the direction, pressure and rate of flow of the hydraulic fluid is determined by the valves 91 and 98. Valves 9! and 98 may be operated in any manner; but it is preferred that they be solenoid operated.

In schematic Figures 4 to 7:

I. A diagonally hatched pipe or area indicates that the fluid therein is at atmospheric or reservoir pressure.

II. A horizontally hatched pipe or area indicates that the fluid therein is at the discharge pressure of pump 83.

III. A dotted pipe or area indicates that the fluid therein i at accumulator pressure. 1

IV. A blank pipe indicates that there is no fluid therein.

For fast operation of the fluid motor I04 in the forward direction to move the back gauge 2III rapidly in the forward direction. the valves 97 and 98 are set in the positions of Figure 4.

In valve 91, port A connected to pipe IE5 is connected to port 2 which is connected by passages IIQ, I21 to valve 98. Port I of valve 91 is connected to passage I28 and also to port P1 which is connected to pipe 94A.

Valve 98 is opened to connect passages I I9l 21 through valve 98 to passages ISM-439a.

The fluid circuit for fluid motor IE4 is then from the discharge port of the pump 83 through passage 9| to the main relief valve 92, through passage 94 into the micro-filter 96, and hence through port I, through passages I28 and 99b, to the fluid motor I04.

The exhaust of fluid motor IN is then through passages 99a and IBM to solenoid valve 98 (B1) entering port P2 and leaving port 2, then through passages I21, H9 to port 2 of solenoid valve 91, and out through port A, passage IE5 and I05 into pressure chamber 13 of the accumulator 82.

The speed of fluid motor IN is thus determined by the difference between the pressure in accumulator chamber I3 as maintained by compression spring 'I! and the pressure exerted by pump 83.

This difference in pressure is maintained at a constant rate since the reverse relief valve III connected by passage I I2 to passage I28 and pipe 991) on one side and by passage III? on the other side to reservoir 8| is biased to maintain passage II2 closed at pump pressure but to connect passages I I2 and I II] at pressures substantially above that of pump 83 to prevent too great a back pressure. The relief pressure at valve III must be higher, however, than the relief pressure at main relief valve 92 to permit the slow operation of the back gaugeZIiI hereinbelow described.

In the operation of a back gauge ZIII, it is necessary to move the back gauge rapidly between cuts, but to slow down the movement of the back gaugeas the end of the movement approaches to prevent coasting of the paper stack beyond'the cutting point when the back gauge stops.

This slow down of the movement of the back gauge is brought about by closing of the ports P2-2 of the solenoid valve 98 (B1), whereby the only remaining path for the exhaust oil from the fluid motor I84 is through passage I25 and I2I to the restricted orifice I20.

This sudden restriction to oil flow would also build up a high pressure in passage I25 unless said pressure may be relieved through cavitation relief valve I22.

This slows down motor IM and hence back gauge EIII. pump 83 which cannot pass through the restricted orifice I26 then discharges through the main relief valve and through pipe 93 into the reservoir 8 I.

Thi is the condition shown in Figure 5 wherein all elements are set for forward operation of the back gauge at slow speed.

When the back gauge 2III reaches the stop position (see Figure 6), valve 91 is moved to connect ports P1 and A and to close the other ports and connections.

The fluid motor I84 is thus cut-off and ceases to operate. Pump 83 is then connected by pipes and elements III, 92, 94, 96, 9M, P1 of 91, A of 91, I05, I86 to the accumulator chamber I3 where it may charge up accumulator chamber 13.

After the back gauge 2III has completed its forward movement, it must be returned to its initial retracted position so that it may start over again with a new stack of paper.

This is accomplished (as seen in Figure '7) by opening valve 98 and by connecting together ports P1 and 2 of valve 91 and connecting ports I and A of valve 91.

The pump 83 will now deliver pressure oil through 9I-92-9496-94a-P1 and 2 of valve e'I-I I9--I2*IP2 and 2' of valve 98-I99a99a into fluid motor I04.

The function of the reverse relief valve is as follows:

When the motor is turning inreverse. and the The excess fluid delivered by the I discharge passage is suddenly blocked by the closing of port I, the momentum of the motor would build up excessive pressure in the passages 95% and 128 and to relieve this condition, the reverse relief valve is provided so that oil may be discharged through passage H2 through valve Ill and passage H0 into the reservoir tank 8|.

Reverse relief valve I ll permits excess pressure to bleed off from pipe I23 during the reverse operation.

By this means, therefore, a simplified easily controlled hydraulically operated mechanism is provided to permit the fast forward movement, slow forward movement, stopping and reverse movement of back gauge 20 l.

The restricted orifice member I20 connected by passage |2l across passages l25-99a and H9 combined with the cavitation relief valve I22 in parallel therewith between these passages serve in a manner well-known in the art of hydraulic mechanism to maintain unimpeded operation of the device.

The function of safety valve I24 is as follows;

When the ports I and 2 of the valve 91 are closed to stop the fluid motor I04, its momentum will build up pressure in passage I25; said pressure may be relieved through safety valve I24. While cavitation relief valve I22 can open, oil flow therethrough would still be blocked at valve 97, the setting of safety valve I24 being considerably higher than that of valve I22.

By the means herein described, the various movements of the back gauge may be automatically controlled by elements which respond to movement of the back gauge to predetermined positions to slow and then stop the back gauge. Valves 9'! and 98 are operated for forward or reverse movement as the case may be.

The valves 91 and 98 may be solenoid operated by means energized in accordance with the disclosure of said Pat. No. 2,628,680 or in any other suitable manner.

In the foregoing I have described my invention solely in connection with specific illustrative embodiments thereof. Since many variations and modifications of my invention will now be obvious to those skilled in the art, I prefer to be bound not by the specific disclosures herein contained but only by the appended claims.

I claim:

1. In a cutting machine having a cutting table,

a back gauge movable longitudinally along said cutting table, a longitudinal screw connected to said back gauge for moving the same, and a hydraulic motor adapted to be connected to drive said screw; the invention which comprises a hydraulic system arranged to drive said hydraulic motor; said hydraulic system comprising a reservoir and a container for fluid under pressure and a pump; first multiple valve control means; a connection through said first valve to conduct pressurized fluid from said pump to said hydraulic motor for driving the motor; a second connection from said container for fluid under pressure through said first valve to the opposite side of said motor; said pump delivering fluid to said motor through said first connection at greater pressure than thefluid delivered through said second connection to drive said motor in one direction at a predetermined speed; a second valve in said first connection; said second valve being normally open to maintain said first connection from said pump to said motor; said second valve being operable to divide the flow in i said first connection, diverting a portion of said able to connect said pump directly to said container for fluid under pressure; disconnecting both the container for fluid under pressure and the pump from the hydraulic motor in order to halt said hydraulic motor.

2. In a cutting machine having a cutting table, a back gauge movable longitudinally along said cutting table, a longitudinal screw connected to said back gauge for moving the same, and a hydraulic motor adapted to be connected to drive said screw; the invention which comprises a hydraulic system arranged to drive said hydraulic motor; said hydraulic system comprising a reservoir and a container for fluid under pressure and a pump; first multiple valve control means; a connection through said first valve to conduct pressurized fluid from said pump to said hydraulic motor for driving the motor; a second connection from said container for fluid under pressure through said first valve to the opposite side of said motor; said pump delivering fluid to said motor through said first connection at greater pressure than the fluid delivered through said second connection to drive said motor in one direction at a predetermined speed; a second valve in said first connection; said second valve being normally open to maintain said first connection from said pump to said motor; said second valve being operable to divide the flow in said first connection, diverting a portion of said flow to the reservoir; said last-mentioned operation reducing the pressure in said first connection to a level slightly above that in the second connection and thereby reducing the speed of said hydraulic motor; said first valve being operable to connect said pump directly to said container for fluid under pressure; disconnecting both the container for fluid under pressure and the pump from the hydraulic motor in order to halt said hydraulic motor; said first valve being operable to reverse said first and second connections to cause a reverse movement of said hydraulic motor.

3. In a cutting machine having a cutting table, a back gauge movable longitudinally along said cutting table, a longitudinal screw connected to said back gauge for moving the same, and a hydraulic motor adapted to be connected to drive said screw; the invention which comprises a hydraulic system arranged to drive said hydraulic motor; said hydraulic system comprising a reservoir and a container for fluid under pressure and a pump; first multiple valve control means; a connection through said first valve to conduct pressurized fluid from said pump to said hydraulic motor for driving the motor; a. second connection from said container for fluid under pressure through said first valve to the opposite side of said motor; said pump delivering fluid to said motor through said first connection at greater pressure than the fluid delivered through said second connection to drive said motor in one direction at a predetermined speed; a second valve in said first connection; said second valve being normally open to maintain said first connection from said pump to said motor; said second valve being operable to divide the flow in said first connection, diverting a portion of said flow to the reservoir; said last-mentioned operation reducing the pressure in said first connection to a level slightlyi above that in the second connection and thereby reducing the speed of said hydraulic motor; said first valve being operable to connect said pump directly to said container for fluid under pressure; disconnecting both the container for fluid under pressure and the pump from the hydraulic motor in order to halt said hydraulic motor; said first valve being operable to reverse said first and second connections to cause a reverse movement of said hydraulic motor, solenoid means for operating said first valve.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 913,853 Rowntree Mar. 2, 1909 Number 10 Number Name Date Howse July 3, 1923 Taylor Mar. 14, 1933 Valiquette May 9, 1933 Lehman Oct. 11, 1938 Eickman Aug. 27, 1940 Fox Jan. 8,1946

FOREIGN PATENTS Country Date Great Britain Mar. 31, 1887 

